Hydraulic valve and hydraulic power device embodying such valves



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Feb; 22, 1949.

Filed March '7, 1946 C. D. WATSON A HYDRAULIC VALVE AND HYDRAULIC POWER DEVICE EMBODYING SUCH VALVES 5 Sheets-Sheet 2 l/V YEN TOR DIN/EL nwrsan,

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ATTORNEY Feb. 22, 1949. c. D. WATSON HYDRAULIC VALVE AND HYDRAULIC POWER DEVICE EMBODYING SUCH VALVES 5 Sheets-Sheet 4 Filed March 7, 1946 \Q- I 0- 9 on \3 D Q .I. r f! I I! I I\! r on\ t. f 1 I: N No; B- 2 v .y +0. 9 w 6- W H n .n nwp Ar NZ, \N\\\\\\\\\\\\\\\\\\\\\\\\ A 2 Q0 0 15 I 2 w// ATTORNEY W GQ C. D. WATSON HYDRAULIC VALVE AND HYDRAULIC POWER DEVICE EMBODYING SUCH VALVES Feb. 22, 1949.

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ATTORNEY Patented Feb. 22, 1949 HYDRAULIC VALVE AND HYDRAULIC POW ER, DEVICE EMBODYING SUCH VALVES Cyril Daniel Watson, Farnborough, England Application March 7, 1946. Serial No. 652,531

In Great Britain March 20, 1945 6 Claims. (01. 121-41) This invention relates generally to hydraulic power devices.

One object of the invention is to provide in a hydraulic power device means whereby positional control of a hydraulic power element of the positive displacement type, such as a displacement pump, jack or vane motor may be effected in accordance with variations of pressure as governed by a selector device.

A further object of the invention is to provide means for effecting the positional control of a hydraulic power element of the above kind in accordance with selected variations of pressure comprising a movable member adapted to be moved by the resultant eifort of a hydraulic pressure selectively controlled by suitable selector means acting against a resilient means associated with the movable component of the power element in a direction to cause the displacement of the said movable component and the associated resilient means in a direction appropriate for annulling the said resultant effort; v

The resilient means preferably comprises a spring abutment which is displaced conformably with the displacement of the movable component.

Another object of the invention is to provide a valve for controlling the connections of a double/ acting hydraulic power element to pressure and return lines comprising a movable member sub jected to the opposed efforts of a selectively controlled hydraulic pressure and a spring whose abutment is displaced conformably with the displacement of the movable component of the power element in such a manner that the resultant of said opposed efforts displaces the movable valve member in the appropriate sense for bringing about a displacement of the said movable component, and hence of the spring abutment, in the appropriate direction for annulling the said resultant effort.

A still further object of the invention is to provide a hydraulic power device comprising a jack, the piston of which is provided with a hollow piston rod and to utilize the changing volume of the interior of said rod to permit correct positioning of the piston in response to selectively controlled variations of the control pressure.

Yet another object of the invention is to provide a self-servoing valve member.

Yet another object is to provide positional selector means for operating the said device comprising a variable pressure reducing valve, for example a ball or other spring loaded valve, controlling the reduction of pressure and a selector member for varying the spring loading.

Yet another object of the invention is to provide a selector device selectively operable to re late the pressure in the "control" pressure line for controlling the movement of a hydraulic power element of the positive displacement type comprising a positional selector control member and a cylinder communicating with the control" pressure line and containing a spring-loaded piston, and a follow-up valve associated with the supply and return pressure lines, the said valve tion and in which synchronism at the end of the stroke is ensured by the provision of blow-oil valves associated with the movable component of each power element.

With the above and other objects in view. reference will now be made to the accompanying drawings, forming part of the specification,

which illustrate, by way of example, various forms of hydraulic power devices embodying the invention and in which:

Figure 1 is a sectional view oi a pair of series operated hydraulic jacks forming power elements and one of which embodiesa positional control valve in accordance with the invention,

Figure 2 is a fragmentary sectional view of the head of the jack, embodying a positional control valve as shown on the lower half of Figure l and showing a modified arrangement of the valve.

Figures 3, 4 and 5 are similar views to Figure 1 but showing respectively further modified constructions of the'control valve incorporated in the lower jack, and Figure 6 shows, diagrammatically, a hydraulic flap operating system for an aircraft, comprising four independent flap sections actuated by three pairs of series operated jacks, as shown in any of Figures 1 to 5, "control" pressure selecting means and their several hydraulic connections.

In Figures 1 to 5, similar reference numerals pistons l2 and I3 respectively connected to hollow piston rods I4 and I5, which project through the right hand ends of the said jacks for connection to themechariism to be operated. The

space below the piston I2 of the jack III, that,

is to say the right hand end of the jack I0, is hydraulically connected to the space above the piston I3 of the jack II, that is to say the left hand end of the jack II, by a, series transfer line I5. The head 20 of the Jack Ill constitutes a housing for the control valve to be hereinafter described, and has four passages formed therein, namely, a passage I8 hydraulically connected by a line I! with the space below the piston I3 ofthe jack II, a passage I9 communicating with the space above the piston I2 of the jack III, a. passage 2| connected externally to the pressure supply line (not shown) and a branched passage 22 connected externally to the return line (also not shown). The inner ends of these four passages open into a cylindrical valve chamber 23 formed in the head 20 coaxially with the jack I and the left hand end of the valve chamber 23 communicates with a fifth passage 24 in the head 20 having an external hydraulic connection to a line by which the control" pressure, which is regulated by a positional selector control device, is applied. The selector device is not shown in Figure 1 but a preferred form is illustrated in Figure 6 to be hereinafter referred to.

Slidable within the valve chamber 23 is a piston valve 25 having annular grooves 26- and 21 and an intermediate land 28. The valve piston is extended to form a rod 29 which is nested coaxially within a sleeve 30 secured to the jack head 20. The sleeve 30, is, in turn, coaxially nested within the piston I2 and the piston rod I4. Near the right hand end thereof the rod 23 is enlarged, at 3 I, to form a plunger slidable in the sleeve 30 and provided with hydraulic seals 32. The right-hand end of the sleeve '30 is closed by a cap 33 through which projects an extension of the rod 29 to terminate in a head 39.

"As will be seen, the sleeve 30, the cap 33, the plunger 3| and the extension of the rod 23 enclose an-annular space 35 which is subjected to the control pressure through the medium of a passage 34 centrally drilled through the vvalve piston 25 and the rod 29. The left hand end of this passage 34 opens into the valve chamber 23 and is thereby in free communication, through the passage 24, with the "contr 0l pressure line, and the right hand end of the passage communicates with the space 35 by means of a side drilling. Back pressure on the face of the plunger 3| opposite to the space 35 is relieved by venting the clearance between the sleeve 30 and the rod 29 to one branch of the return passage 22 through a drilling 36 in the head 20.

v The jack piston I2 slides on the sleeve 30, being provided with a hydraulic seal 38 to prevent leakageof fluid past the piston I2.

Between the outside of the sleeve 30 and the inside of the piston rod I4 is a clearance which is occupied by helical compression spring 40, the

right end of which abuts on the head 39 of the rod 29 and the left hand end of which abuts on an internal shoulder 4| formed in the piston I2.

The above described mechanism the following manner:

Admission of the "control pressure to the space 35 behind the plunger 3 Hands to move the rod 23 and the valve piston to the left, so as to establish communication, through the annular groove 21, between the passage 2| carrying the operating pressure and the passage I3 communieating with the space above the piston I2 of the jack III; at the same time,'the' annular groove 28 establishes communication between the left hand branch of the passage 22 and the passage I8, thus placing the space below the piston I3 of the jack II in communication with the return circuit via the line I I. Since the series transfer line I6 is always open, pressure will be applied above both the pistons I2 and I3, causing them to move to the right.

operates in The effort of the control" pressure in the space I acting on the back of the plunger 3| is, however, opposed by the effort of the spring 40 acting on the head 39, and, as thepiston I2 moves to'the right, the spring 40 is compressed, thus in- The pistons I2 and I3 are also provided with blow-oil valves 42, 43, 44 and 45 respectively, the purpose of which will hereinafter be referred to.

creasing its effort on the head 33 until a balance is struck between the control pressure and the spring effort. -When this occurs the valve piston 25, 29 will move to the right until the land 23 and theleft hand end of the piston valve 25 close the passages 2| and 22 and thereby hydraulically lock the system. If the control pressure, applied through the passage 24, is then increased (by the selector device), the effort of the spring 40 will again be overcome and the valve piston will move to the left so as to connect the space above the jack I2 and below the jack I3 to pressure and return respectively, as before, thus causing the pistons I2 and I3 to move further to .the right. until balance is again established between the opposed hydraulic and spring forces acting on the valve piston 25, 29. Conversely, if the control pressure is reduced, the action will be reversed, (the pressure circuit being now established through the annular groove 26 and the passage I8, and the return circuit through the passage I9, the annular I groove 21 and the right-hand branch of the passage 22), and the piston I2 and I3 will move to the left, until balance is again established between the hydraulic and spring forces acting on the valve piston 25, 23, when the system will again become locked through the valve piston moving into the aiautral position and closing the passages 2| and It will, therefore, be appreciated that, for every selected value of the control" pressure, there corresponds a definite position of the piston I2 along its stroke in which the spring 40 is just sufilciently compressed to balance the control pressure applied to the valve piston and maintain the latter in equilibrium in its neutral position. Therefore, the position of the piston I2 along its stroke can be uniquely selected by selectin; the appropriate control pressure to be applied through the passage 24.

As long as the series transfer line I5 is full of fluid and is maintained under pressure, the piston I3 will exactly follow the movements of the piston I2 and when the system is hydraulically locked in mid-stroke, by the control valve 25, 29 being in its neutral position, the piston I3 will mainta n its correct relationship with respect to the piston I2, provided there is no leakage past the piston seals. Perfect synchronism of the pistons I2 and I3 is obtained at the ends of the stroke by the provision of blow-off valves 42, 43, 33 and 45 in the manner described in the specification accompanying my copending patent application Serial No. 652,530 filed March 7, 1946, applied for jointly with Reginald Charles Samuel Mansell, but now abandoned. If lack of synchronism develops when the system is locked for a prolonged period in mid-stroke, owing to leakage past the piston seals, synchronism can be readily restored by bringing the system to one end or the other of its stroke and returning it again to the desired mid-stroke position.

In the modified arrangement shown in Figure 2, the construction of the valve is the same as that shown in Figure 1 except that the passage 24 carrying the "control pressure communicates with an annular recess 24a surrounding the left hand end of the piston valve 25, and the control bore 34 communicates through a ported cross passage 54a with the annular recess24a. This arrangement is advantageous in that it increases the effective area on which the control pressure acts. In the construction shown in Figure 1, the contro pressure, supplied through the passage 24, is not only applied to the right hand endof the piston by the passage 34, but is also applied in the opposite direction to the end of the valve 25 in the valve chamber 23, so that the efiective area for moving the valve 25 is the difference between the annular area of the piston 3| and the area of the end of the valve 25. Since, however, a back pressure may momentarily be built up on the face of the piston 3| opposite to the space 35, it is desirable to increase the effective area on which the control pressure acts, and this is obtained by the arrangement shown in Figure 2.

A further modification is shown in Figure 3. In this arrangement, the operating piston, indicated at 3la, of the valve rod is arranged in an enlargement of the bore of the valve body 20. Balance of the back pressure is obtained through a central bore 94 in the valve rod 25, 29 providing communication between the space 23 at the left hand end of the valve rod and the space 96 at the left hand side of the piston I2. The space 95 is, in this arrangement, in communication with the interior of the jack rod I4 through an opening 91, which has the advantage that the whole area of the jack piston I2 is available for the application of the operating pressure for movement of the jack from left to right.

A passage 95 communicating with an additional external line is provided for exhausting the space behind, that is to say, to the left of, the control piston 3Ia.

The provision of an additional external line, such as is required in the arrangement just described in connection with Figure 3, is avoided in the construction of the valve shown in Fi ure 4, which construction offers the further advantage that the changing volume of the interior of the jack piston rod It, as the jack piston travels along its stroke, is utilised to promote correct positioning of the jack piston in response to selectively controlled variations of the control pressure. As shown in Figure 4, the piston valve 25 is of larger diameter than the rod 29 and the "control pressure is supplied through the passage 24 to the right hand end of the valve 25 where it acts over the whole of the area of the piston valve 25. There is no central bore in the valve 25 or in the rod 29 and the left hand end thereof in the space 23 is open to atmosphere. The space between the tube 30 and the valve rod 29 is open to the interior of the jack piston rod I4 which is, therefore, under the contro pressure. When the selected control pressure is altered, the valve 25 acts, as before, to

6 enable the jack piston to be moved until the control pressure on the valve 25 is balanced by the action of the spring 40 and, during this movement, the volume of the interior of the jack pis- 5 ton rod I4 is altered, so that a considerable volume of fluid has to be passed through the supply passage 24 and this exercises a volume control over the rate of movement of the piston I2, thereby ensuring a greater accuracy in the positioning of the latter when the condition of equilibrium is restored. With this arrangement there is no back pressure acting on the valve.

A still further modified arrangement is illustrated in Figure 5, the valve being, in this case, a self-servoing valve. The valve portion of the rod 25, 29 slides within a valve sleeve 98 which is formed with ports I05 and I06 communicating, through passages I01 and I00 respectively, with opposite ends of the valve sleeve, which, when the valve portion of rod is moved, are opened by the grooves 26 and 21, one to the passage 2| and the other to the branched passage 22, to

cause pressure fluid to bepassed to one end of the said valve sleeve and to be exhausted from 25 the other end, so that the valve sleeve follows the movement of the valve portion of rod 25.

The valve sleeve 98 is formed with annular grooves I09, H0 and III, with intermediate lands I I2 and H3, controlling the ports connected with 30 the passages I8, I9, 2| and 22 in the same way as the valve portion of rod 25 in the previously described constructions and a spring 99 is provided to stabilize the sleeve in the position in which the said ports are closed, with pressure at the right hand end of the sleeve 98 balancing the spring load, when the jack is stationary. In order to increase the effectiveness of the action of the control pressure, the valve stem 25, 29

is provided, in the arrangement shown in this figure, with a piston I00 sliding in an enlargement of the valve body 20, and springs IOI and I02 acting on either face of the piston I00. The

control pressure is fed to the right hand face of this piston I00 through the passage 24 and the space, to the left of the piston I00, is connected to the atmosphere through a passage I03. Leakage of pressure fluid past the piston I00 is prevented by a hydraulic seal I04.

The arrangement, by enabling the diameter of the valve portion of the rod 25, 29 to be made very small, minimises the effects of friction whilst the diameter of the valve sleeve 98 can be made large enough for the passages, conveying the fluid for actually operating the jack, to be made of generous dimensions. It is to be understood, however, that the piston I00 may be omitted and, instead, any of the means described in connection with the previous arrangements shown in Figures 1-4, for applying the control pressure to the valve, may, if desired, be employed.

The self-servoing action of the valve, herein described, greatly increases the accuracy with which the jack piston I2 is positioned corresponding to any selected "control pressure.

Referring now to Figure 6., this figure illustrates the application of series operated jacks with selective pressure-responsive positional control, as illustrated in, and described with reference to, any of the preceding figures, to an aircraft flap system having four independent flap sections operated by three pairs of series operated jacks. A flap arrangement of this kind is particularly suitable for a folding wing aircraft in which two inboard fiap sections are separated from two out- 75 board flap sections by the wing folding hinges.

7 In the figure, the port and starboard inboard flap sections are shown at 48 and 41 respectively and the port and starboard outboard flap 'sections at 48 and 49 respectively. These flap sections are operated through levers by three pairs of series operated jacks, each pair being similar to a pair of jacks l8 and II shown in Figures 1,

3, 4 or 5, and having similar control arrangements. The three master" Jacks 58, 5| and-52 are constructed similarly to the jack l8 and the three "slave" jacks 59, 54 and 55 are constructed similarly to the-Jack II of those figures. One pair 58 and 53 ,of series operated jacks are applied to the inboard flap sections 46 and 41, the jack 58 operating the flap section 46 and the jack 58 operating the fiapsection 41; the second pair of series operated jacks 5| and 54 are applied to the port outboard flap section 48 and the third pair of series operated jacks 52 and 55 are applied to the starboard outboard flap section 49.

The master and slave jacks of each pair are respectively interconnected by series transfer lines 56, 51 and 58 corresponding to the series transfer line l6 of the previous figures. The lower ends of the slave jacks 53, 54 and 55 are connected with the heads of their master jacks 58, 5| and 52 by hydraulic lines 59, 68 and 6| corresponding to the line I! of the aforesaid figures.

Each master jack has three external hydraulic connections corresponding respectively to the connections of the passages 2|, 22 and 24, of which passages 2| carries the main supply pressure, 22 is connected to the return line and 24 carries the "control pressure. The supply pressure connections of the three master jacks are indicated at 65, 66 and 61, the return line connections are indicated at 68, 69 and i8 and the control pressure connections at 12 and 13. The supply pressure'connections 65, 66 and 61 are branched from a common supply pressure line 62, the return pressure connections 68, 69 and '38 are branched from a common return line 63 and the control pressure connections ll, 12 and 13 are branched from a common control pressure line 64. It will, therefore, be seen that the three pairs of; jacks are operated in parallel.

The pressure in the control line 64 is regulated by a positional selector device comprising a fixed cylinder 14 containing a slidable piston 15, the cylinder space 16, above the head of the piston '85, being in communication with the control pressure line 64 through a branch line H. The rear of the piston 15 is loaded by means of a helical compression spring 19 and the piston is 'provided with a piston rod I8 which extends outside the cylinder, the outer end of the rod 18 having connected thereto a valve body 88 in which is slidable a piston valve member 8| provided with adjustable stops Ma and 8|b. The valve body 881s provided with three external ports connected respectively to the control pressure line 64 and the lines 82 and 83 which are respectively branches of the aforesaid common supply pressure line 62 and the aforesaid common return line 63. The valve member has a single annulus serving to connect the control pressure line 64 either with the supply pressureline 82 or with the return line 83 according to the position of the valve member 8| relative to the valve body 88; in the neutral position of the valve member, both lines 82 and 83 are shut-off from the control pressure line 84. The stem of the valve member 8| carries a head 84 enclosed in a spring box 85 having bufier springs88 and 81 on both sides of the head 84. A rod 88, formed integral with the spring box 85, is pivoted at 9| to a selector lever 89 which is mounted on a fixed pivot 98 and works in a quadrant 92 provided with suitable notches forlocating the said selector lever 88.

Movement of the selector lever 89 in either direction is communicated, through the rod 88. the spring box 96, the buffer springs 86 and 81 and the head 84, to the valve member 8|, which is, thereby, shifted to put the control pressure line 84 in communication with the supply pressureline 82 or the return line 88, according to the direction of movement of the selector lever.

The consequent variation of pressure in the control pressure line 64 is communicated to the cylinder space 16 by the branch line 11, causing the piston 15, the rod 18 and the valve body 88 to be displaced in the direction appropriate for cancelling the movement of the valve member 8| relative to the valve body 88. The permissible relative movement between the valve member 8| and the valve body 88 is small, being limited by the stops 8|a and 8| b and, if the selector lever 89 is displaced to a considerable extent, the lost motion between it and the valve member 8| is .inftially taken up by the springs 86 and 61; as,

however, the piston I5 and the valve body 88 move under the influence of the changing pressure in the space I6, the valve member 8| follows up this movement and takes up the lost motion between it and the selector lever 89 until the springs 86 and 81, in the spring box 85, are in equilibrium, after which further movement of the piston 15 brings the valve body 80 into the neutral position relative to the valve member 8|, thus cutting off the control pressure line 64 from the supply or return line, as the case may be, and stabilizing the pressure therein and in the cylfinder space 76. It will be appreciated that, when the system is stabilised, the piston 15 is in equilibrium under the opposed efforts ofthe pressure in the control pressure line and the compression spring 19. so that the pressure in the control pressure line corresponds to the desure-line 84 and this, in turn, by means of the control valves incorporated in the master jacks, as hereinbefore described with reference to Figures 1-5, determines the position of the jack pistons and consequently the setting of the flaps.

The rate at which pressure builds up, or is let down, in the "control pressure line 64, and, therefore, the rate at which the pistons of the flap operating jacks are moved, depends on the discharge rate of the valve unit 88, 8|. This depends on the maximum port openings of the valve unit 88. 8|, which are determined by the stops 8|a and 8| b; the rate of operation of the whole system can, therefore, be regulated by suitably adjusting the stops 8|a, 8|b, and, by applying different adjustments to the said stops 8|a, 8| b, the rate of operation of the whole systemfor the two opposed directions of motion, namely, the raising and lowering of the flaps 46-48, may be made to differ so .that any desired timing for raising and. lowering-the said -01 the thin operating jacks, is compensated by the valve unit 80, 8| remaining slightly selected" that is to say slightly ofi" the neutral position so that the seepage is made up We trickle discharge through the valve unit 80, M. The above-mentioned relative displacement of the valve unit 80, 8| from the neutral position and the consequent displacement of the equilibrium position of the piston I5, relative to the selector lever 89, is of a very small order and has no material eflect on the pressure established in the control pressure line for a given position of the said selector lever, because the total relative movement of the valve body 80 and the valve member 8|, as defined by the stops Illa and Bib, is quite small in comparison with the total travel of the piston 15 in the cylinder 14. The valve unit 80, 8| will, therefore, compensate for seepage in any part of the contro pressure circuit regardless'of the rate of seepage, provided the latter is less than the full discharge rate of the said valve unit 80, 8!, without sub- 1o and said piston slidin rod surrounding, said sleeve; a movable valve member slidable in said bore in said head for controlling the supply of pressure fluid to said Jack;

a rod-like extension on said valve member, said extension having a smaller diameter than-the internal diameter of, and being slidable within, said sleeve; a piston element located adjacent the rear end of said extension, and said valve member and said extension having a bore therein extendin from the front thereof to the rearof said piston element; an abutment on the rear end or said extension; a spring located within said hollow piston rod and surrounding said sleeve, said spring hearing at one end against said piston abutment and at the other end against said abutment on said extension, and means for applying a. selectively controlled hydraulic pressure through said bore to the rear of said piston elestantial detriment to the accuracy of positional selection, but the greater is the rate of seepage the more sluggishly will the system operate. This, however, can be corrected by readjusting the stops Bid and Nb (within the limits of their eiiective adjustability) to give a quicker rate of operation.

Although the discharge rate of .the valve unit 80. 8| determines the rate of displacement of the selector piston I5. and hence of the valve assembly Bil, 8i and 84, the resilient connection, provided by the spring box 85 and its contained springs 86 and B1, enables the selector lever 89 to be moved as quickly as may be desired. To enable the selector lever to be so moved throughout its complete range, the spring box 85 must accommodate the full range of movement of the selector lever 89 without coil binding of the said springs 86 and 81 contained therein.

I claim: l. A device of the kind referred to comprising in combination: a hydraulic jack; a movable piston and a hollow piston rod in said jack; an abutment on said piston; a head on said jack. said head having a bore therein; a sleeve on said head,

ment on said extension against the action of said spring whereby the resultant effort applied to said piston element moves said valve member in a direction to cause displacement of said jack piston and said piston abutment in a direction aphead having a bore therein; a sleeve on said head,

said sleeve extending within the body of said jack and said piston sliding on, and said hollow piston rod surrounding, said sleeve; a movable valve member slidable in said bore in said head for controlling the supply of pressure fluid to said lack;

of said bore in said head; an abutment on the rear rod surrounding, said sleeve; a movable valve member slidable in said bore in said head for controlling the supply of pressure fluid to sa d jack; a rod-like extension on said valve member slidable within said sleeve; an abutment on the rear end of said rod-like extension; a spring located within said hollow piston rod and. surroundin said sleeve, said spring hearing at one and against said piston abutment and at the other end aga nst said abutment on said extension, and means for applying a selectively controlled hydraulic pressure to said valve member against the action of said spring whereby the resultant effort applied to said extension moves said valve member in a direction to cause displacement of saidpiston and said piston abutment in a direction appropriate for annulling said resultant efiort.

2. A device of the kind referred to comprising in combination a hydraulic jack; a movable piston and a hollow piston rod in said jack; an abutment on said piston; a head on said Jack, said head having a bore therein; sleeve on said head. said sleeve extending within the body of said jack end of said rod-like extension; a spring located within said hollow piston rod and surrounding said sleeve, said spring bearing at one end against said piston abutment and at the other end against said abutment on said extension, and means for applying a hydraulic pressure through said annular recess and said bore in said extension to the rear of said piston element on said extension against the action of said spring whereby the resultant efiort applied to said piston element moves said valve member in a direction to cause displacement of said jack piston and said piston abutment in a direction appropriate for annulling said resultant efiort.

4. A device of the kind referred to comprising in combination: a hydraulic jack, a movable piston and hollow piston rod therein; an abutment on said piston; a head on said jack, said head having a bore therein; a sleeve on said head, said sleeve extending within the body of the jack and said piston sliding on, and said hollow piston rod surrounding, said sleeve; a movable valve member slidable within said head for controlling the supply of pressure fluid to said jack; a rod-like extension on said valve member, said extension being of smaller diameter than the diameter oi said valve member, whereby said valve member, constitutes a piston element, and said extension extending within said sleeve and being of smaller diameter than the interior of said sleeve, so as to leave an annular space therebetween open to the interior of said piston rod; an abutment on the rear end of said extension; a spring located within said hollow piston rod and surrounding said sleeve, said spring bearing at one end against on, and said hollow piston said pistonabutment and at the other end against said abutment on said extension, and means for applying a hydraulic pressure to the rear of said valve piston element against the action of said spring whereby the resultant eflort applied to said valve piston moves said valve member in a direction to cause displacement of said Jack piston and said spring abutment thereon in a direction appropriate for annulling said resultant effort.

5. A device of the kind referred to comprising in combination: a hydraulic power element having a movable component therein; a valve body associated with said power element, said valve body having a bore therein; a movable valve member, for controlling the supply of main pressure fluid to said power element, slidable in said bore, said ,valve member comprising valve portion proper and a valve sleeve within which said valve portion is slidable and said sleeve having a pair of passages and associated ports therein connecting the bore of said sleeve with the opposite ends of said sleeve respectively; a resilientmeans assoclated with said movable component and said member under the resultant effort applied thereto, said ports and passageways are put into communication with said main pressure fluid supply whereby pressure fluid is passed to one end of said sleeve and exhausted from the other to cause 7 12 the said sleeve to follow the movement of said valve portion and the arrangement being such that the resultant efiortwpplied to said valve member moves said valve. sleeve in a direction to a cause displacement of said movable component and said resilient means in a direction appropriate for annulling said resilient eflort.

6. A device according to claim 5 and including specified.

CYRIL DANIEL WATSON.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS FOREIGN PATENTS Country Date Great Britain Dec. 7, 1937 Great Britain Jan. 26, 1940 Number Number 

